Code punching machine



H. E. MORRIS CODE PUNCHING MACHINE May 22, -1962 3 Sheets-Sheet 1 FiledJan. 25, 1961 May 22, 1962 H. E. MORRIS 3,035,763

CODE PUNCHING MACHINE Filed Jan. 25, 1961 3 Sheets-Sheet 2 IN VEN TOR.

May 22, 1962 H. E. MoRRxs 3,035,763

CODE PUNCHING MACHINE Filed Jan. 25, 1961 3 Sheets-Sheet 3 jig. 14

IN V EN TOR.

United States Patent O 3,035,763 CODE PUNCHING MACHINE Howard E. Morris,Arlington Heights, lll., assignor, by

mesne assignments, to Victor Comptometer Corporation, Chicago, Ill., acorporation of Illinois Filed Jan. 25, 1961, Ser. No. 84,875 7 Claims.(Cl. 234-128) The present invention relates to code punching orperforating machines and is concerned particularly with problems whicharise in the perforation of a very wide recording body of indefinitelength which is indexed or stepped through a code punching station.

One object of the inventio-n is to provide an improved code punchingmachine which will operate eiciently and dependably at high speed topunch data in code in a very wide recording body of indefinite length.

Another object is to provide a code punching machine adapted to punchcode in a wide recording body and having a new and improved constructionwhich brings the recording body to a Vcomplete stop in each of asuccession of recording positions with reference to a punching stationwhile at the same time providing for very fast advancement lof therecording body to successive recording positions ina manner whicheffects a smooth acceleration `and a smooth deceleration of the body asit advances from one recording position to another.

Another object is to provide an improved code punching machine in whichhigh speed intermittent advancement of a recording bodyto a successionof punching positions is provided by improved means which maintains apositive control of the position of the recording body at all times nohold the body completely still in each successive punching position ofthe body and to effect quick advancement of the recording body betweensuccessive punching positions in a manner that avoids the application ofimpact loads to recording body indexing structure in the machine byproviding for mutual engagement of coacting parts of the indexingstructure before the parts are subjected to recording body advancingforces.

A further object is to provide an improved code punching machine of thecharacter recited in which operating forces transmitted between coactingparts of the recording body indexing structure in the machine are spreadover extensive mutually engaged surface areas of the coacting parts toavoid stress concentrations and effectively minimize wear even thoughthe machine is operated at high speed.

Other `objects and advantages Will become apparent from the followingdescription of the exemplary embodiment of the invention illustrated inthe drawings, in which:

FIGURE 1 is a fragmentary plan view illustrating the organization ofmajor components of the code punching machine forming the illustratedembodiment of the invention;

FlG. 2 is a fragmentary vertical sectional view taken generally alongthe line 2 2 of FIG. l;

FlG. 3 is a fragmentary vertical sectional with reference to the line 33 of FIG. 1;

FIG. 4 is a simplified sectional view similar to FIG. 3 but illustratinga different operating phase of the recording body indexing mechanismshown;

FIG. 5 is a fragmentary sectional view similar to FIG. 4 butillustrating a still different phase in the operation of the mechanisms;

FiG. 6 is an exploded perspective view of indexing elements incorporatedinto the machine; and

FIG. 7 is an end view of the assembly of operating cams used in indexingthe recording body in the machine.

Referring to the drawings in greater detail, the code punching machine1G forming the exemplary embodiment View taken lCC Y.

of the invention illustrated is adapted to punch data in y code in avery wide recording body 12 of indenite length. In this instance, therecording body 12 is formed by a strip of recording paper which isapproximately sixteen inches wide. The width of the recording body 12 isdetermined by considerations which relate largely to the variousfunctions the recording body is designed to serve and cannot besubstantially controlled by the design of the code punching machine.

ln the present instance, the recording body 12 consists of a connectedseries of utility bills which extend longitudinally across the width ofthe recording body. Each bill must have sufficient length to accommodateinformation adequate for billing a customer by mail and to provide spacefor recording data in punched code.

ln the code punching machine 16, the wide recording body 12 is movedalong a path which carries a portion of the body through a punchingstation 14 defined by the punching machine. In passing through the codepunching or perforating station 14, the recording body 12 is stepped orindexed across a deck or table 16 of a punching head 18 which iscontrolled by electrical code signals supplied to a bank of punchcontrol solenoids 20.

The punching or perforating head 18 is designed to record data in atelegraphic code, such for example as the Teletype code. The head 1S, assuch, is formed of a, conventional construction requiring no specificdescription here. A bank `of perforating punches 22 is selectivelyoperated in response to coded electrical signals to punch a transverseline of apertures in the portion of the recording body 12 located in thepunching station 14.

The recording body 12 is held stationary in the recording station 14while coding punches 22 are moved through the recording body to punch acoded line of apertures 24 in the body. After the punches 22 arewithdrawn, the recording body 12 is indexed or stepped to its nextrecording position which brings an imperforate portion of the body intoalignment with the punches 22. This intermittent indexing of therecording body 12 to a succession of recording positions in which thebody is stopped and punched in code is characteristic of the mode ofoperation Aof code punching machines which record data in punched codein this manner.

However, special problems arise in the punching of wide recordingbodies, such for example, as the sixteen inch wide recording body 12which is coded in the machine 10.

In the interest of production eiciency, it is important that therecording body 12 be intermittently indexed and punched in code at arapid operating speed. However, the matter of effecting a rapidintermittent indexing of a very Wide recording body 12 presents a sourceof problems which are not encountered in the indexing of narrowrecording bodies, such as the narrow recording tapes in which data iscommonly punched in code.

In order to rapidly index and properly position the wide recording body12 with reference to the punching station :14 it is necessary to providerelatively massive Isupport structure `for the recording body, whichsupport structure must be indexed with the body. As illustrated, in thedrawings, the two marginal side edges of the wide recording body 12 aretrained over two widely spaced sprocket wheels 2S, 3i) rotatably fixedto a common indexing shaft 32. Sprockets on the wheels 23, 30 fit intosprocket openings 34 in the marginal side edges of the recording body 12to effect a positive positioning of the recording body with reference tothe sprocket wheels.

Because of the great width of the recording body 12, it is necessary toprovide support to the recording body between the sprocket wheels 28,30. This is effected by means of a plurality of support wheels orrollers 35, 36, 3S, 44) nonrotatably iixed to intermediate portions ofthe shaft 32 as shown in FIGS. 1 and 2, to fnctionally engage therecording body y12, which is trained over the intermediate supportrollers in the same manner that it is trained over the sprocket wheels,as shown in FIG. 3.

The recording body 12 is intermittently advanced with reference to thepunching station 14 by intermittent rotary indexing movement of theindexing shaft 32. This shaft together with the sprocket wheels 28 and3G, the intervening support ,wheels 35, 36, 38 and 4i), and the meansconnected with the shaft 32 to effect rotary indexing lmovement of theshaft have in the aggregate a relatively large rotary inertia. Thisrotary inertia, which tends to resist rotary acceleration anddeceleration of the shaft 32, is cumulative with the rather substantialinertia of the wide indexing body 12.

During the actual punching of the recording body, all the structurewhich moves with the recording body is held stationary. To advance therecording body 12 from one indexed position to another, it is necessaryto accelerate the body and the structure rotatable with the shaft 32from a standing st-art to a maximum indexing speed and then decelerateall this mass to a complete stop.

In order to achieve an eicient operating speed of the code punchingmachine it is necessary that the total elapsed period for eachsuccessive punching cycle be reduced to only a small fraction of asecond. Moreover, the total time consumed in indexing the recording bodyfrom one punching positioning to the next should be the lowest possiblefraction of the total operating period for each punching cycle in orderto maximize the operating efficiency of the machine. The effect of theseconsiderations is to place a great premium on reducing the time requiredto advance the recording body to its successive recording positions.

In the machine 10, the shaft 32, which controls the position of therecording body 12, is operated by a gear 42 drivingly connected to oneend of the shaft as shown in FIGS. 1 to 3 and having a diameterapproximately equal to that of the sprocketV wheels 28, 30. Controlledindexing movement of the gearV 42 is powered by a rotary cam shaft 44parallel to the shaft `=32. The cam shaft 44 is energized by an electricmotor 46 connected through a speed reducing transmission 48 and a clutch49 Vwith the cam shaft as shown in FIG. 1. The clutch 49 is controlledby a solenoid 51 to effect starting and stopping of the shaft 44independently of acceleration and decelera- 'tion of the driving motor46.

One end of the shaft 44 projects through a support bracket 48 whichprovides support to both the shaft 44 and the shaft 32.

The end of the shaft 44 which projects beyond the bracket 48 supportsthree coaxial operating cams 50, 52, 54 disposed in fixed predeterminedrotary positions relative to each other and nonrotatably fixed -to theshaft 44. The three cams 50, 52, and 54 are axially spaced somewhat fromeach other as shown in FIG. 2. The middle one 52 of the three cams 50,52 and 54 serves as a power driving or actuating cam for physicallyadvancing the gear 42 intermittently to index the recording body 12 tosuccessive recording positions.

As will presently appear, the three cams 56, V52, 54 cooperate withcoacting parts to effect two complete indexing cycles of the recordingbody positioning structure for each complete revolution of the cam shaft44.

As best shown in FIG. 7, the power driving or actuating cam 52 has adouble Iobed form designed to produce two advancing movements of thegear 42 for each revolu.- tion of the shaft 44. The cam surface on theperiphery of the cam 52 engages a following roller 56 on one end of aswingable feed actuator 58, which is pivotally supported at its oppositeend for swinging movement vabout the rotary axis of the shaft 32. Asshown, the swingable actuator 58 has a generally U-shape and comprisestwo parallel legs 60, 62, FIG. 6, which embrace the gear 42, FIG. 1, andhave apertured support ends which are pivoted on the shaft 32.

The cam follower 56 is held in engagement with the cam 52 by the actionof a tension spring 64 as will presently appear. The feed actuator 58follows the cam 52 to oscillate between a retracted position shown inFIG. 5 and an advanced position shown in FIG. 3 through an angle equalto the angle through which the gear 42 is to be advanced to index therecording body 12. The cam 52, moreover is shaped to effect dwelling ofthe feed actuator 58 in each of its two extreme positions and to effecta quick swinging movement of the actuator between its extreme positionwith smooth acceleration and deceleration of the actuator movement.

The portion of the peripheral cam surface on each of the cams 50, S2, 54which is activated in a single complete indexing cycle extends only 180degrees around the cam and merges with an identical por-tion of the camsurface which extends around the second half of the cam.

The periphery of the cam 52 denes a pair of inner dwelling surfacesegments 70, 72 spaced 180 degrees from each other around the cam. Eachof these surfaces has a center of curvature coinciding with the yaxis ofthe shaft 44 and extends around the cam through a radial angle ofapproximately twenty degrees.

Each of the cam surface segments 70, 72 coacts with the cam follower S6to provide yfor dwelling of the feed actuator 58 in its retractedposition illustrated in FIG. 5. Dwelling of the feed actuator 58 in itsVadvanced position illustrated in FIG. 3 is provided for by a pair ofouter, dwelling surface segment 74, 76 of the cam 52 located ondiametrically opposite sides of the cam between the dwelling surfaces70, 72, as shown lin FIG. 7. Each outer dwelling surface segment 74, 76has a `center of curvature coinciding with the yaxis of the shaft 44 andextend circumferentially through a radial angle of approximately twentydegrees.

The cams 50, 52, and 54 are rotated in the counter- Iclockwise directionwith reference to FIGS. 3, 4, 5 and 7. Two diametrically opposedactuator retracting cam surface segments 78, 80 on the cam 52 extendfrom the outer dwelling ysurfaces 74, 76 respectively to the respectiveinner dwelling surfaces 72, 70 as shown in FIG. 7. These surfaces areshaped to effect a smooth acceleration and deceleration of the actuator58 to quickly return the actuator from its advanced position to itsretracted position.

Two actuator `advancing cam surface portions 82, 84 are formed on thecam 52 in diametrically spaced relation to each other and extend fromthe inner dwelling surfaces 7 0, 72 respectively to the respective outerdwelling surfaces 74, 76 and serve individually to smoothly accelerateand decelerate the feed actuator 58 to swing from its retracted positionto its advanced position.

To review the operation of the cam 52, we may start with the assumptionthat the feed actuator 58 is dwelling in its extended position with thefollower 56 moving along the outer dwelling surface 74. As the followerroller 56 moves olf the surface 74 onto the surface 78, the actuator 58is quickly but smoothly accelerated and then smoothly decelerated tolocate the actuator 58 in its retracted position as the roller moves offthe surface 78 onto the surface 72. The actuator 58 dwells in itsretracted position until the roller moves from the surface 72 onto thesurface 84, which effects a smooth acceleration of the actuator in -afeeding or advancing direction. The actuator 58 is smoothly Adeceleratedlas the roller 56 moves Ialong the trailing end of the surface 84 to thesurface 76 which causes the actuator to again dwell in its advancedposition. This cyclic action of the actuator 58 is repeated as theroller 56 moves on -along the surfaces 80, 70 and 82 back to the surface74. Y

The swinging movements of the :actuator 58 in a recording body indexingdirection are transmitted to the gear 42 through a feed pawl 90pivotally supported on the actuator 58 between the roller 56 and thepivotally supported end of the actuator.

The feed pawl 90 defines -a plurality of locking elements or teeth 92,three in this instance, disposed in opposing relation to the gear 42 andadapted to interfit with opposing teeth on the gear upon swinging of thepawl into engagement with the gear.

The previously mentioned biasing spring 64 connects with a laterallyextending -anchoring element 94 on the pawl 90 to apply a rotary biasingforce to the pawl tending to cause it to swing about its support pivot96 on the actuator 58 to engage the teeth `elements 92 on the pawl withthe gear 42, FIG. 3. The reaction of the spring 64 on the pawl 90 istransmitted through the pivot 96 to continuously hold the actuator 58 inengagement with the cam 52 as previously described.

Movement of the feed pawl 90 into and out of engagement with the gear 42is controlled by a cam follower 98 rigidly connected to the pawl 90 toswing with the pawl about the pivot 96 on the actuator 58. A roller 100on the follower 98 bears directly on the periphery of the cam 50, whichis shaped in relation to the position of the follower 98 and in relationto the cam 52 to engage the pawl 90 with the gear 42 while the actuator58 is dwelling in its retracted position and to disengage the pawl 90from the ygear 42 while the actuator 5S is dwelling in its advancedposition.

Having reference to FIG. 7, when the feed -actuator roller 56 is inengagement with the outer dwelling surface 74, for example, the feedpawl cam following roller 100 moves over a rising cam surface 102 on thecam 50, which l disengages the feed pawl 90 from the gear 42, FIG. 4. Bythe time the -actuator roller 56 reaches the end of the dwelling surface74 to move onto the retracting surface 78, the feeding pawl controlroller 100 'has moved onto a raised cam surface 104 on the cam 50. Thecam surface 104 is conformed to the cam surface 7S to hold the feed pawl90 in its released position throughout the return movement of theactuator 58 to its retracted position.

After the actuator roller 56 has reached the inner dwelling surface 72,the feed pawl control roller 100 travels down a declining cam surface106 on the cam 50 to allow the spring 64 to reengage the feed pawl 90with the gear 42 before the roller 56 reaches the end of the dwellingsurface 72, FIG. 5. Hence, the pawl 90 is fully engaged with the gear 42before the actuator 58 starts to advance.

As the roller 56 moves along the surface 84 to advance the actuator 58,the feed pawl control roller 100 moves along a surface 108 of lthe cam50 which conforms to the surface 84 of the cam 52 to maintain fullengagement of the pawl 90 with the gear 42 until the actuator 58 reachesits fully advanced position.

As the roller 56 continues along the outer dwelling surface 76, the feedpawl control roller 100 continues along a second pawl disengagingsurface 110 on the cam S which is identical to the previously mentioneddisengaging surface 102 on the cam 50. From the surface 110, the roller100 continues along Vsurface portions 112, 114 and 116 of the cam 50which form identical counterparts of the previously mentioned camsurface portions 104, 106, and 108.

A positive control of the rotary position of the indexing gear 42 ismaintained at all times by positively locking the gear in a stationaryposition after it has been advanced to a new position and before thefeed pawl 90 is released from the gear. Moreover, the gear 42 is heldstationary by the positive locking means until the feed pawl 90 is againfully engaged with the gear to effect the next successive rotaryadvancement of the gear, whereupon the locking of the gear 42 isrepeated cyclically in timed relation to operation of the feed pawl. g

. The gear 42 is positively locked in each indexed position to which itis moved by means of a locking pawl 120 swingably supported on a pivot122. The locking pawl ,120 denes a plurality of locking teeth elements124, three in this instance, adapted to mesh in locking engagement withopposing teeth on the gear 42 upon engagement of the pawl with the gear.The pawl is urged toward engagement with the gear by means of thepreviously mentioned spring 64 which is connected between a springanchor 126 on the pawl 120 and the previously mentioned anchor 94 on thepawl 90.

Movement of the pawl 120 into and out of engagement with the gear 42 iscontrolled by the coaction of a cam following roller 123 on the pawl 120with the previously mentioned cam 54.

As shown in FiG. 7, the cam 54 defines two locking cam engaging surfaces130, 132 located on diametrically opposite sides of the cam and spacedapart by two intervening locking cam release surfaces 134, 136. Thesurfaces 130, 132 and 134, 136 on the cam 54 have positions which arecorrelea'ted to the position of the coacting roller 128 and to thepositions of the previously described cam surfaces on the cams 50 and S2to produce the desired synchronization `of the locking pawl 120 with thefeed pawl 90.

The locking pawl release surface 136 is designed to hold the pawl 120 inits gear releasing position as the actuating roller 56 moves over theindexing surface S2 of the cam S2, FiG. 3. When the roller 56 reachesthe outer dwelling surface 74, the locking pawl control roller 123 movesfrom the surface 136 down a declining surface 13S on the cam 54 to reachthe lock engaging surface 132 and effect engagement of the locking pawl1.20 before the feed pawl control roller 100 moves up the surface 192 onthe cam 50 to release the feed pawl 9o.

The locking pawl control roller 128 remains in engagement with the camsurface 132 until the feed pawl control roller 100 has passed over thedeclining cam surface 106 to reengage the feed pawl 90 with the gear 32.After the pawl 90 is fully engaged with the gear 32 and before theadvancing roller 56 starts up the advancing surface S4, the locking pawlroller 128 moves up a raising cam surface 140 onto the lock releasingcam surface 134, which holds the locking pawl in released position onlyuntil the advancing roller 56 reaches the next dwelling surface 76,whereupon the roller 12S moves down a declining cam surface 142 to againreengage the locking pawl.

The locking pawl control surface is identical to the surface 132 andconnects with the cam surface 136 through a rising cam surface portion144 identical with the rising cam surface portion whereby the cyclicaction of the locking pawl 120 is performed twice during each revolutionof the shaft 44.

The indexing structure thus described is capable of applying powerfulrotary indexing torque to the indexing shaft 32 to eect a high speedintermittent indexing of the recording body 12 without imposingexcessive stress on the indexing structure. The feed pawl 90 is fullyengaged with the gear 42 and occupies a stationary position withreference to the gear and with reference to the feeding actuator 5Sbefore indexing force is applied through these fully engaged parts toadvance the gear 42.

This full engagement of the coacting parts with each other beforeindexing force is applied to any of the parts avoids impact loading ofthe structure which would tend to overstress the parts and tend to causeexcessive Wear on the indexing structure. Moreover, the gear actuatingforces transmitted between the feed pawl 90 and the gear 42 aredistributed over rather extensive mutually engaged -surfaces of the feedpawl teeth elements 92 and the opdata in punched code in a recording-body 12 which can have an extensive width.

It will be understood that the invention is not necessarily limited touse of the particular construction illustrated but includes the use ofvariants and alternatives within the scope of the invention as definedin the claims.

The invention is claimed as follows:

l. A code punching machine adapted to punch coded data into a Wide sheetof recording paper and comprising, in combination, means delining apunching station, code punching means for punching coded informationinto a recording sheet in said punching station, two widely spacedsprocket wheels yadapted to simultaneously engage a wide recording sheetto determine the position of the recording sheet with reference to saidpunching station, a drive shaft connecting said sprocket wheels, aplurality of recording paper support rollers mounted on said shaft, arotary driving and locating gear connected in driving relation, to saidshaft to continuously conform the rotary position of the latter with therotary position of the gear, a rotary cam shaft, a feed cam on said camshaft, a feed actuator mounted for swinging movement about the axis ofsaid gear and including a cam follower engaging said feed cam, meanscontinuously biasing said actuator follower into engagement with thefeed cam, said feed cam being shaped to effect swinging movement of saidactuator between forward and retracted positions with motionlessdwelling of the actuator in each of said positions and with smoothacceleration and deceleration of the actuator between said positions, afeed pawl cam on said cam shaft, a feed pawl pivotally mounted on saidactuator and including gear teeth adapted to mesh with teeth of saidgear, a cam follower on said feed pawl 'biased into engagement with saidfeed pawl cam, said feed pawl cam being shaped to effect engagement ofthe feed pawl with said gear during stationary dwelling of said actuatorin its retracted position, and to eifect disengagement of the feed pawlfrom said gear during stationary dwelling of the actuator in itsadvanced position, a holding pawl cam on said cam shaft, a pivotedholding pawl defining a plurality of teeth thereon adapted tosimultaneously engage a plurality of teeth on said gear and including acam `follower biased into engagement with said holding pawl cam, saidholding pawl cam being shaped to effect disengagement of the holdingpawl from said gear during stationary dwelling of said actuator in theretracted position thereof and subsequent to engagement of said feedpawl with the gear and to effect engagement of the holding pawl with thegear while said actuator is stationary in its advanced dwelling positionand prior to release of the feed pawl from the gear, and each of saidcams having a .double lobed construction vwhich eects two completeadvancing cycles of said gear for each revolution of said cam shaft.

2. A code punching machine adapted to punch data in code in a recordingbody and comprising, in combination, means defining a punching station,code punching means for punching information in code ito a recordingbody in said punching station, recording body driving means adapted toengage a recording body and determine the position of the recording bodywith reference to said punching station, a rotary driving wheelconnected in driving relation to said recording body driving means tovcontinuously determine the position of the latter, a rotary feed cam, afeed actuator including a cam follower continuously engaging said feedcam and being mounted for movement by said feed cam between forward andretracted positions, a rotary feed pawl cam rotated in synchronism withsaid feed cam, a feed pawl mounted on Vsaid actuator for intermittentengagement with said wheel and including a cam follower continuouslyengaging said feed pawl cam, said feed pawl cam being shaped to eectdriving engagement of the feed pawl with said wheel when said actuatoris in its retracted position and to eifect disengagement of the feedpawl from said wheel when said actuator is in its advanced position, arotary holding pawl cam rotated in synchronism with feed cam and saidfeed pawl cam, a holding pawl supported for intermittent holdingengagement with said wheel and including a cam follower continuouslyengaging said holding pawl cam, and said holding pawl cam being shapedto effect disengagement of the holding pawl from said wheel when saidactuator is in the retracted position thereof and to effect holdingengagement of said wheel by said holding pawl when said actuator is inits adv-anced position.

3. In a code perforating machine, the combination of means defining aperforating station, code perforating means for perforating a recordingbody located in said station, rotary sprocket means adapted to coactwith a recording body to determine the position of the body withreference to said perforating station, a rotary driving gear connectedin driving relation to said sprocket to determine the rotary position ofthe latter, a pivoted holding pawl defining a plurality of gear teethelements thereon adapted to mesh with opposing teeth on said gear,spring means urging said pawl in a direction Vfor engaging said teethelements thereon with said gear, a rotary cam shaft, a cam on said shaftcoacting with a cam follower on said pawl to control engagement anddisengagement of the latter with said gear in timed relation to rotationof said shaft, an oscillatory driving element mounted for swingingmovement about the axis of said gear, spring means coacting with saiddriving element to bias the latter rotatably in one direction, a secondcam on said cam shaft coacting with a follower on said driving elementto effect controlled oscillation of said driving element through an`angle corresponding to desired rotary angles of indexing movement ofsaid gear, a feed pawl pivotally mounted on said driving element anddefining a plurality of gear teeth elements adapted to engage opposingteeth on said gear, said feed pawl being biased to urge said gear teethelements thereon toward engagement with said gear, a third cam on saidshaft coacting with a follower on said Ifeed pawl to effect movement ofthe latter into and out of engagement with said gear in synchronism withrotation of said shaft, said third cam being shaped in relation to saidsecond cam to effect full engagement of said feed pawl with said gearprior to swinging of said driving element in a gear advancing directionand to effect disengagement of said feed pawl from said gear at thecompletion of gear advancing movement of said driving element and beforethe driving element is retracted in the opposite direction, and saidiirst cam lbeing shaped in relation to said second and third cams toeffect engagement of said holding pawl with said gear subsequent tocompletion of the advancing movement of said driving element and priorto the release of said feed pawl from said gear and to effectdisengagement of said holding pawl from said gear subsequent tore-engagement of said feed pawl with said gear and prior to subsequentadvancement of said power driving element.

4. A code punching machine adapted to punch coded data into a widerecording body and comprising, in combination, means defining a punchingstation, code punching means for punching information in code into arecording body in said punchig station, rotary recording body drivingmeans adapted to engage a -wide recording body to determine the positionof the recording -body with reference to said punching station, a rotarydriving gear connected in driving relation to said driving means tocontinuously determine the rotary position of the latter, a rotary feedcam, a feed actuator mounted for swinging movement about the axis ofsaid gear and including a cam follower biased -into engagement with saidfeed cam, said feed cam being shaped to elect swinging movement of saidactuator between forward and retracted positions with dwelling of theactuator in each of said positions, a rotary feed pawl cam operated insynchronism with said feed cam, a feed pawl mounted on said actuator forIintermittent engagement with said gear and including a cam followerbiased into engagement with said feed pawl cam, said feed pawl cam beingshaped to effect engagement of the feed pawl with said gear duringdwelling of the actuator in its retracted position and to eectdisengagement of the feed pawl from said gear during dwelling of theactuator in its advanced position, a rotary holding pawl cam operated insynchronism =with said feed cam and said feed pawl cam, a holding pawlsupported for intermittent engagement with said gear and including a camfollower biased into engagement with said holding pawl cam, and saidholding pawl cam being shaped to effect disengagement of the holdingpawl from said gear during dwelling of the actuator in the retractedposition thereof and to eect engagement of the holding pawl with thegear while said actuator is dwelling in its advanced position.

5. In a code perforating machine, the combination of means dening aperforating station, code perforating means lfor perforating a recordingbody located in said station, rotary means adapted to coact with arecording body to determine the position of the body with reference tosaid perforating station, a rotary driving gear connected in drivingrelation to said rotary means to determine the rotary position of thelatter, a holding pawl movably supported for intermittent engagementwith said gear, a rotary power shaft, a rst cam driven by said shaft andcoacting with said pawl to effect engagement and disengagement of thelatter with said gear, an oscillatory driving element, means including asecond cam driven by said shaft and coacting with said driving elementto effect controlled oscillation of said driving element, a feed pawlmounted on said driving element for intermittent engagement with saidgear, a third cam driven by said shaft and coacting with said feed pawlto effect movement of the latter into and out of driving engagement withsaid gear in synchronism with rotation of said shaft, said third cambeing shaped in relation to said second cam to effect engagement of saidfeed pawl with said gear prior to advancement of said driving element ina gear advancing direction and to effect disengagement of said feed pawlfrom the gear at the completion of -gear advancing movement of saiddriving element, and said first cam being shaped in relation to saidsecond and third cams to effect engagement of said holding pawl withsaid `gear subsequent to completion of the advancing movement of saiddriving element and prior to retraction of the driving element and toeffect disengagement of said holding pawl from said gear prior tosubsequent advancement of said power driving element.

6. In a code perforating machine, the combination of means defining aperforating station, code perforating means for perforating a recordingbody located in said station, rotary means adapted to coact with arecording body to determine the position of the body with reference tosaid perforating station, a rotary driving wheel connected in drivingrelation to said rotary means to determine the rotary position of thelatter, a holding pawl movably supported for intermittent engagementwith said wheel, a

rotary shaft, a first cam driven by said shaft and coacting with saidpawl to effect engagement and disengagement of the' latter ywith respectto said wheel, an oscillatory driving element, means including a secondcam driven by said shaft and coacting with said driving element toeffect controlled oscillation of the latter, a feed pawl mounted on saiddriving element for intermittent engagement with said wheel, a third camdriven by said shaft and coacting with said feed pawl to effect movementof the latter intoand out of engagement with said wheel in synchronismwith rotation of said shaft, said third cam being shaped in relation tosaid second cam to effect full engagement of said feed pawl with saidwheel prior to advancement of said driving element in a wheel advancingdirection and to effect disengagement of said feed pawl from said wheelat the completion of wheel advancing movement of said driving elementand before the driving element is retracted in the opposite direction,and said first cam being shaped in relation to said second and thirdcams to effect engagement of said holding pawl with said wheelsubsequent to compietion of the advancing movement of said drivingelement and prior to the release of said feed pawl from said gear and toeffect `disengagement of said holding pawl from said wheel subsequent tore-engagement of said feed pawl with said wheel and prior to subsequentadvancement of said power driving element.

7. In a code punching machine adapted to punch data in code in a widerecording body, the combination of means defining a punching station,code punching means for punching information in code into a recordigbody in said punchig station, two widely spaced indexing wheels adaptedto simultaneously engage a wide recording body to determine the positionof the recording body with reference to said punching station, a rotarydriving gear connected in driving relation to said indexing wheels, anactuator swingably mounted for oscillation about the axis of saiddriving gear, a rotary cam shaft, a feed cam on said cam shaft coactingwith said actuator and being shaped to effect oscillation of theactuator between advanced and retracted positions and to effect dwellingof the actuator in each of said positions as an incident to rotation ofsaid cam shaft, a feed pawl mounted on said actuator in coactingrelation to said gear to transmit to said gear successive advancingmovements of said actuator from said retracted position to said advancedposition thereof, a holding pawl vmovably supported to intermittentlyengage said gear in locking relation thereto, and a holding pawl cam onsaid cam shaft coacting with said holding pawl and being shaped todisengage the holding pawl from said gear during stationary dwelling ofsaid actuator in the retracted position thereof and to re-engage theholding pawl with said gear while said actuator is dwelling in itsadvanced position.

References Cited in the le of this patent UNITED STATES PATENTS2,293,077 Potts Aug. 18, 1942

